US8469669B2 - Cover disk for a closed impeller - Google Patents

Cover disk for a closed impeller Download PDF

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Publication number
US8469669B2
US8469669B2 US12/919,553 US91955309A US8469669B2 US 8469669 B2 US8469669 B2 US 8469669B2 US 91955309 A US91955309 A US 91955309A US 8469669 B2 US8469669 B2 US 8469669B2
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United States
Prior art keywords
cover disk
front side
radius
rotor
cover
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related, expires
Application number
US12/919,553
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English (en)
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US20110008160A1 (en
Inventor
Henning Ressing
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MAN Energy Solutions SE
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MAN Diesel and Turbo SE
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Publication date
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Assigned to MAN DIESEL & TURBO SE reassignment MAN DIESEL & TURBO SE ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RESSING, HENNING
Publication of US20110008160A1 publication Critical patent/US20110008160A1/en
Application granted granted Critical
Publication of US8469669B2 publication Critical patent/US8469669B2/en
Assigned to MAN ENERGY SOLUTIONS SE reassignment MAN ENERGY SOLUTIONS SE CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: MAN DIESEL & TURBO SE
Expired - Fee Related legal-status Critical Current
Adjusted expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2216—Shape, geometry
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors

Definitions

  • the invention is directed to a cover disk for a closed rotor of a radial flow machine or diagonal flow machine, for example, a radial compressor or radial expander, particularly of a turbocompressor, a rotor with a cover disk of this kind, and a flow machine with a rotor of this kind.
  • DE 37 09 518 C2 and DE 41 13831 A1 disclose closed rotors with a cover disk in which an outer surface of the cover disk remote of the flow channel has a radial offset adjoined by a conical portion of constant wall thickness so that there is a local maximum in the wall thickness of the cover disk between the suction port and the flow outlet in the radial offset.
  • this is not discussed in DE 37 09 518 C2 or in DE 41 13831 A1.
  • the present invention is directed to a cover disk for a closed rotor of a radial flow machine or diagonal flow machine which defines a flow channel and whose wall thickness has a local maximum along the profile mean line of the meridional cross section of the cover disk between a first front side and a second front side of the cover disk, and wherein an outer surface of the cover disk remote of the flow channel has in the area of this local maximum a convex curvature with a radius (R 2 . 2 ) whose ratio (R 2 . 2 /D 2 ) to an outer diameter (D 2 ) of the rotor is within a range from 0.05 to 0.5 (0.05 ⁇ R 2 .
  • the present invention is based on the insight that a local convexity or bulge in the outer surface of the cover disk leads to a rotor geometry which can reduce stresses at critical structural areas in connection with a corresponding curvature of the outer surface of the cover disk during centrifugal forces occurring in operation.
  • a convex curvature with a radius whose ratio to an outer diameter of the rotor is within a range of 0.05 to 0.5 is provided in the area of a local maximum of the wall thickness of the cover disk at the outer surface thereof.
  • the maximum stresses are reduced by 20% and, further, advantageously no longer occur at the critical end region of the cover disk, but rather in a middle connection portion between the rotor disk and rotor blade.
  • a cover disk according to the invention is provided for a closed rotor of a radial flow machine or diagonal flow machine, for example, a radial compressor or radial expander, particularly of a turbocompressor, and can be produced, e.g., primary-shaped or machined, integral with the blading.
  • a cover disk according to the invention can also be connected, e.g., riveted, soldered and/or welded, to the blading.
  • the two constructions can be advantageously combined as is known from DE 41 13 831 A1 with radially divided rotor blades, wherein a rotor part is formed integral with the cover disk and another rotor part is nondetachably connected thereto.
  • the cover disk together with a two-dimensional or three-dimensional blading and the rotor disk, defines a flow channel for a fluid to be conveyed, compressed or expanded.
  • the cover disk has a profile mean line or skeleton line which extends in the middle between the outer surface of the cover disk remote of the flow channel and an inner surface of the cover disk facing the flow channel.
  • the cover disk has a local maximum along this profile mean line between a first front side and a second front side.
  • the first front side can be, for example, an inlet side or suction side
  • the second front side can correspondingly be an outlet side or pressure side.
  • the cover disk according to the invention has a bulge on its outer surface between the inlet and outlet.
  • the outer surface has a convex, outwardly curved curvature with a radius whose ratio to the outer diameter of the rotor is within a range of 0.05 to 0.5.
  • the largest diameter or the rated diameter of the rotor is the outer diameter of the rotor.
  • the bulge results in a more favorable distribution of mass so that the maximum stresses occurring in operation are reduced. Accordingly, higher rotor speeds, longer lifetimes and/or the use of weaker and, therefore, cheaper materials are possible. Further, the occurrence of maximum stresses on structurally unfavorable locations such as the outer circumference of the cover disk in the region where it is connected to the rotor blading, which is often carried out as a weld, can be avoided or such stresses reduced by the convex curvature with the radius ratio according to the invention.
  • the ratio of the radius to the outer diameter is preferably between 0.1 and 0.4, particularly preferably between 0.15 and 0.3. This results in rotors which are particularly free from stresses.
  • the convex curvature of the outer surface of the cover disk merges toward the first front side and/or second front side into a concave curvature so that the outer edge of the meridional cross section has an inflection point before and/or after the local maximum in which the curvature changes its mathematical sign.
  • Outer surfaces of this kind with areas which are curved in opposite directions one or more times are particularly stress-free and can be manufactured easily.
  • the concave curvature can have a radius toward the first front side which is smaller than the radius of the convex curvature in the region of the local maximum. Accordingly, a cover disk according to the invention can be axially compact because the convex, gently curved area can slope relatively steeply in the axial direction in the concave area with the smaller radius.
  • the wall thickness of the cover disk decreases continuously toward the second front side.
  • the cover disks known from DE 37 09 518 C2 and DE 41 13831 A1 with conical outer portions of constant thickness the external mass and, therefore, the mass moment of inertia, the weight, and the production costs can be reduced in the present case, and the continuous reduction, particularly a reduction with a substantially constant radius of curvature, provides for an advantageous distribution of stresses.
  • the cover disk terminates toward its outer circumference in a concavely curved portion which adjoins the convexly curved portion in the area of the local maximum.
  • this includes constructions in which the outer circumferential edge of the outer surface itself is interrupted or is formed with a small convex radius in some other way.
  • FIG. 1 is a meridional cross sectional view through half of a cover disk according to an embodiment of the present invention.
  • FIG. 2 is a meridional cross sectional view through half of a cover disk according to the prior art.
  • FIG. 2 shows a half-sectional view of the meridional cross section of a cover disk 1 ′ of a radial rotor (not shown) according to the prior art such as is known, for example, from FIG. 12 of DE 198 33 033 A1.
  • this cover disk 1 ′ defined by inner surface 1 . 1 ′ and outer surface 1 . 2 ′ decreases along the profile mean line of the meridional cross section between a first front side 2 ′ of the cover disk (at left in FIG. 2 ) defining a suction port of a radial flow machine (not shown) and a second front side 3 ′ of the cover disk (at right in FIG. 2 ) which lies axially opposite from the first front side 2 ′ and which forms a flow outlet from the flow channel defined by the cover disk 1 ′ continuously from the suction port 2 ′ to the flow outlet 3 ′.
  • FIG. 1 shows the meridional cross section of a cover disk 1 of a radial rotor (not shown) according to an embodiment of the present invention with a first front side 2 (at left in FIG. 1 ) through which a radial flow machine (not shown) takes in fluid axially and, axially opposite to this first front side 2 , a second front side 3 of the cover disk (at right in FIG. 1 ) from which the fluid exits radially from the flow channel which is defined by the cover disk 1 and rotor blades (not shown) and a rotor disk (not shown) carrying these rotor blades.
  • An inner surface 1 . 1 facing the flow channel has three convexly curved areas with radii of curvature R 1 . 1 , R 1 . 2 and R 1 . 3 .
  • the radius is indicated, respectively, by an arrow directed from a center of curvature to the surface in FIG. 1 .
  • an outer surface 1 . 2 of the cover disk 1 opposite the inner surface 1 . 1 has an non-curved area parallel to a longitudinal axis of the rotor (dash-dot lines in FIG. 1 ). This area merges into a concave area with a relatively small radius of curvature R 2 . 1 , the wall thickness of the cover disk 1 narrowing to a local minimum in its perpendicular bisector.
  • Adjoining this concave area is a portion which curves away from the flow channel and which has a convex curvature with a radius R 2 . 2 which is greater than the radius of curvature R 2 . 1 . Because of the change from a concave to a convex curvature, the centers of curvature lie on opposite sides of the outer surface 1 . 2 as is indicated by the different arrow directions in FIG. 1 .
  • the convex area in turn merges again in direction toward the second front side 3 into a concave area having a radius of curvature R 2 . 3 in which the wall thickness of the cover disk 1 decreases continuously toward the second front side.
  • the wall thickness along the profile mean line of the meridional cross section of the cover disk 1 has a local maximum between the first front side 2 and the second front side 3 .
  • the outer surface 1 . 2 has a convex curvature with radius R 2 . 2 whose quotient to an outer diameter D 2 of the rotor is: R 2.2 /D 2 ⁇ 0.22.
  • the maximum stresses occur at the transition (not shown) from the rotor blade to the rotor disk and no longer in the area of the second front side 3 of the cover disk 1 . Further, the absolute value of the maximum stress at a defined speed load decreases by 20%.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US12/919,553 2008-03-10 2009-03-10 Cover disk for a closed impeller Expired - Fee Related US8469669B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102008013432 2008-03-10
DE102008013432A DE102008013432A1 (de) 2008-03-10 2008-03-10 Deckscheibe für ein geschlossenes Laufrad
DE102008013432.5 2008-03-10
PCT/EP2009/001722 WO2009112242A2 (de) 2008-03-10 2009-03-10 Deckscheibe für ein geschlossenes laufrad

Publications (2)

Publication Number Publication Date
US20110008160A1 US20110008160A1 (en) 2011-01-13
US8469669B2 true US8469669B2 (en) 2013-06-25

Family

ID=40952901

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/919,553 Expired - Fee Related US8469669B2 (en) 2008-03-10 2009-03-10 Cover disk for a closed impeller

Country Status (6)

Country Link
US (1) US8469669B2 (ja)
EP (1) EP2222962B1 (ja)
JP (1) JP5175363B2 (ja)
CN (1) CN101970883B (ja)
DE (1) DE102008013432A1 (ja)
WO (1) WO2009112242A2 (ja)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3933209A1 (en) * 2020-06-30 2022-01-05 Mitsubishi Heavy Industries Compressor Corporation Impeller of rotating machine and rotating machine
US20240255000A1 (en) * 2021-06-25 2024-08-01 Weir Minerals Australia Ltd Centrifugal Pump Impeller With Tapered Shroud

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104564802B (zh) * 2015-01-06 2017-02-22 浙江理工大学 一种带有减阻槽的无蜗壳离心通风机
JP7161424B2 (ja) 2019-02-26 2022-10-26 三菱重工コンプレッサ株式会社 インペラ及び回転機械

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2305136A (en) 1941-01-31 1942-12-15 Wright Aeronautical Corp Centrifugal blower construction
US2392858A (en) * 1943-03-08 1946-01-15 Gen Electric High-speed rotor for centrifugal compressors and the like
US3887295A (en) * 1973-12-03 1975-06-03 Gen Motors Corp Compressor inlet control ring
US20060280610A1 (en) 2005-06-13 2006-12-14 Heyward John P Turbine blade and method of fabricating same

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB407633A (en) * 1932-10-01 1934-03-22 Hermann Foettinger Improvements in or relating to blading for centrifugal pumps and other machines having rotors with blades co-operating with flowing fluids
US2344444A (en) * 1940-03-29 1944-03-14 Malczewski Jeremi Construction of turbomachines
CN86210682U (zh) * 1986-12-29 1987-10-07 中国科学院工程热物理研究所 离心泵
DE3709518C2 (de) 1987-03-23 1995-01-19 Hilge Philipp Gmbh Laufrad
DE4113831A1 (de) 1991-04-27 1992-10-29 Klein Schanzlin & Becker Ag Geteiltes laufrad
JPH08219001A (ja) * 1995-02-08 1996-08-27 Hitachi Ltd フランシス型ポンプ水車
US6255752B1 (en) 1997-07-26 2001-07-03 Allweiler Ag Mounting for a turbo-machine rotor and its use
JP2001329993A (ja) * 2000-05-19 2001-11-30 Matsushita Electric Ind Co Ltd ポンプの羽根車
US20040136825A1 (en) * 2001-08-08 2004-07-15 Addie Graeme R. Multiple diverter for reducing wear in a slurry pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2305136A (en) 1941-01-31 1942-12-15 Wright Aeronautical Corp Centrifugal blower construction
US2392858A (en) * 1943-03-08 1946-01-15 Gen Electric High-speed rotor for centrifugal compressors and the like
US3887295A (en) * 1973-12-03 1975-06-03 Gen Motors Corp Compressor inlet control ring
US20060280610A1 (en) 2005-06-13 2006-12-14 Heyward John P Turbine blade and method of fabricating same

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3933209A1 (en) * 2020-06-30 2022-01-05 Mitsubishi Heavy Industries Compressor Corporation Impeller of rotating machine and rotating machine
US11493054B2 (en) * 2020-06-30 2022-11-08 Mitsubishi Heavy Industries Compressor Corporation Impeller of rotating machine and rotating machine
US20240255000A1 (en) * 2021-06-25 2024-08-01 Weir Minerals Australia Ltd Centrifugal Pump Impeller With Tapered Shroud

Also Published As

Publication number Publication date
JP5175363B2 (ja) 2013-04-03
US20110008160A1 (en) 2011-01-13
CN101970883A (zh) 2011-02-09
JP2011509373A (ja) 2011-03-24
EP2222962A2 (de) 2010-09-01
WO2009112242A2 (de) 2009-09-17
DE102008013432A1 (de) 2009-09-17
WO2009112242A3 (de) 2009-11-05
CN101970883B (zh) 2013-12-25
EP2222962B1 (de) 2017-12-27

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